Hydraulics and Pneumatics by A.Parr 2nd Edition

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Hydraulics and Pneumatics

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Hydraulics and Pneumatics A technician's and engineer's guide Second edition A n d r e w Parr MSc., CEng., MIEE, MlnstMC ~E I N E M A N N OXFORD BOSTON JOHANNESBURG MELBOURNE NEW DELHI SINGAPORE

Butterworth-Heinemann is an imprint of Elsevier Linacre House, Jordan Hill, Oxford OX2 8DP, UK 30 Corporate Drive, Suite 400, Burlington, MA 01803, USA First edition 1991 Reprinted 1992, 1993, 1995 Second edition 1998 Paperback edition 1999 Reprinted 2000 (twice), 2002, 2003, 2004, 2005 (twice), 2006 Copyright 9 1991, 1998, Andrew Parr. Published by Elsevier Ltd. All rights reserved The right of Andrew Parr to be identified as the author of this work has been asserted in accordance with the Copyright, Designs and Patents Act 1988 No part of this publication may be reproduced, stored in a retrieval system or transmitted in any form or by any means electronic, mechanical, photocopying, recording or otherwise without the prior written permission of the publisher Permissions may be sought directly from Elsevier's Science & Technology Rights Department in Oxford, UK: phone: (+44) (0) 1865 843830; fax: (+44) (0) 1865 853333; email: [email protected]. Alternatively you can submit your request online by visiting the Elsevier web site at http://elsevier.com/locate/permissions, and selecting Obtaining permission to use Elsevier material Notice No responsibility is assumed by the publisher for any injury and/or damage to persons or property as a matter of products liability, negligence or otherwise, or from any use or operation of any methods, products, instructions or ideas contained in the material herein. Because of rapid advances in the medical sciences, in particular, independent verification of diagnoses and drug dosages should be made British Library Cataloguing in Publication Data Parr, E. A. (Eric Andrew) Hydraulics and pneumatics: a technician's and engineer's guide. - 2nd ed. 1. Hydraulics 2. Hydraulic engineering 3. Pneumatics I. Title 621.5'1 Library of Congress Cataloging-in-Publication Data Parr, E. A. (E. Andrew) Hydraulics and pneumatics: a technician's and engineer's guide Andrew Parr. 2nd ed. p. cm. Includes index 1. Hydraulic machinery - Handbooks, manuals, etc. 2. Pneumatic Machinery- Handbooks, manuals, etc. I. Title TJ840.P27 98-22010 621.5' 1-dc21 CTP ISBN-13:978-0-7506-4419-9 ISBN-10:0-7506-4419-2 For information on all Butterworth-Heinemann publications visit our website at books.elsevier.com Printed and bound in Great Britain 06 07 08 09 10 10 9

Contents /x P reface 7 9 1 Fundamental principles 11 Industrial prime movers 14 A brief system comparison 16 An electrical system 17 A hydraulic system 21 A pneumatic system 23 A comparison 28 Definition of terms 28 Mass and force 29 Pressure 31 Work, energy and power Torque Pascal's law Pressure measurement Fluid flow Temperature Temperature scales Temperature measurement Gas laws

vi Contents 2 Hydraulic pumps and pressure regulation 34 Pressure regulation 39 Pump types 42 Gear pumps 42 Vane pumps 45 Piston pumps 46 Combination pumps 50 Loading valves 51 Filters 52 3 Air compressors, air treatment and pressure regulation 56 Compressor types 59 Piston compressors 60 Screw compressors 63 Rotary compressors 64 Dynamic compressors 66 Air receivers and compressor control 67 Air treatment 70 Stages of air treatment 72 Filters 72 Air dryers 73 Lubricators 76 Pressure regulation 78 Relief valves 79 Non-relieving pressure regulators 80 Relieving pressure regulators 80 Service units 83 4 Control valves 84 Graphic symbols 87 Types of control valve 90 Poppet valves 90 Spool valves 92 Rotary valves 96 Pilot-operated valves 96

Check valves Contents vii Pilot-operated check valves Restriction check valves 98 101 Shuttle and fast exhaust valves 103 Sequence valves 106 Time delay valves 107 Proportional valves 108 Servo valves 109 Modular valves and manifolds 122 Cartridge logic valves 125 5 Actuators 126 Linear actuators 130 Construction Mounting arrangements 130 Cylinder dynamics 135 140 Seals 140 Rotary actuators 143 Constructional details 146 Application notes 149 Speed control Actuator synchronisation 152 Regeneration 152 Counterbalance and dynamic braking 156 Pilot-operated check valves 160 Pre-fill and compression relief 160 Bellows actuator 162 163 6 Hydraulic and pneumatic accessories 166 Hydraulic reservoirs 167 Hydraulic accumulators 167 Hydraulic coolers and heat rechangers 169 Hydraulic fluids 174 Pneumatic piping, hoses and connections 175 180

viii Contents 183 Hydraulic piping, hosing and connections 185 186 7 Process control pneumatics 188 Signals and standards 190 The flapper-nozzle 191 Volume boosters 193 The air relay and the force balance principle 197 Pneumatic controllers 198 Process control valves and actuators 201 204 Flow control valves 206 Actuators 207 Valve positioners 207 Converters 208 I-P converters P-I converters 213 Sequencing applications 213 221 8 Safety, fault-finding and maintenance 222 Safety 224 Cleanliness 236 Fault-finding instruments 239 Fault-finding Preventive maintenance Index

Preface Machines should work, people should think The IBM Pollyanna Principle Practically every industrial process requires objects to be moved, manipulated or be subjected to some form of force. This is generally accomplished by means of electrical equipment (such as motors or solenoids), or via devices driven by air (pneumatics) or liquids (hydraulics). Traditionally, pneumatics and hydraulics are thought to be a mechanical engineer's subject (and are generally taught as such in colleges). In practice, techniques (and, more important, the fault- finding methodology) tend to be more akin to the ideas used in elec- tronics and process control. This book has been written by a process control engineer as a guide to the operation of hydraulic and pneumatics systems. It is intended for engineers and technicians who wish to have an insight into the components and operation of a pneumatic or hydraulic system. The mathematical content has been deliberately kept simple with the aim of making the book readable rather than rigorous. It is not, therefore, a design manual and topics such as sizing of pipes and valves have been deliberately omitted. This second edition has been updated to include recent develop- ments such as the increasing use of proportional valves, and includes an expanded section on industrial safety. Andrew Parr Isle of Sheppey ea_parr @compuserve, com

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I Fundamental principles Industrial prime movers Most industrial processes require objects or substances to be moved from one location to another, or a force to be applied to hold, shape or compress a product. Such activities are performed by Prime Movers; the workhorses of manufacturing industries. In many locations all prime movers are electrical. Rotary motions can be provided by simple motors, and linear motion can be obtained from rotary motion by devices such as screw jacks or rack and pinions. Where a pure force or a short linear stroke is required a solenoid may be used (although there are limits to the force that can be obtained by this means). Electrical devices are not, however, the only means of providing prime movers. Enclosed fluids (both liquids and gases) can also be used to convey energy from one location to another and, conse- quently, to produce rotary or linear motion or apply a force. Fluid- based systems using liquids as transmission media are called hydraulic systems (from the Greek words hydra for water and aulos for a pipe; descriptions which imply fluids are water although oils are more commonly used). Gas-based systems are called Pneumatic systems (from the Greek pneumn for wind or breath). The most common gas is simply compressed air. although nitrogen is occa- sionally used. The main advantages and disadvantages of pneumatic or hydraulic systems both arise out of the different characteristics of low density compressible gases and (relatively) high density

2 Hydraulics and Pneumatics incompressible liquids. A pneumatic system, for example, tends to have a 'softer' action than a hydraulic system which can be prone to producing noisy and wear inducing shocks in the piping. A liquid-based hydraulic system, however, can operate at far higher pressures than a pneumatic system and, consequently, can be used to provide very large forces. To compare the various advantages and disadvantages of electri- cal pneumatic and hydraulic systems, the following three sections consider how a simple lifting task could be handled by each. A brief system comparison The task considered is how to lift a load by a distance of about 500 mm. Such tasks are common in manufacturing industries. An electrical system With an electrical system we have three basic choices; a solenoid, a DC motor or the ubiquitous workhorse of industry, the AC induc- tion motor. Of these, the solenoid produces a linear stroke directly but its stroke is normally limited to a maximum distance of around 100 mm. Both DC and AC motors are rotary devices and their out- puts need to be converted to linear motion by mechanical devices such as wormscrews or rack and pinions. This presents no real problems; commercial devices are available comprising motor and screw. The choice of motor depends largely on the speed control requirements. A DC motor fitted with a tacho and driven by a thyristor drive can give excellent speed control, but has high main- tenance requirements for brushes and commutator. An AC motor is virtually maintenance free, but is essentially a fixed speed device (with speed being determined by number of poles and the supply frequency). Speed can be adjusted with a vari- able frequency drive, but care needs to be taken to avoid overheating as most motors are cooled by an internal fan connected directly to the motor shaft. We will assume a fixed speed raise/lower is required, so an AC motor driving a screwjack would seem to be the logical choice.

Fundamental principles 3 Neither type of motor can be allowed to stall against an end of travel stop, (this is not quite true; specially-designed DC motors, featuring good current control on a thyristor drive together with an external cooling fan, can be allowed to stall), so end of travel limits are needed to stop the drive. We have thus ended up with the system shown in Figure 1.1 com- prising a mechanical jack driven by an AC motor controlled by a reversing starter. Auxiliary equipment comprises two limit switch- es, and a motor overload protection device. There is no practical load limitation provided screw/gearbox ratio, motor size and con- tactor rating are correctly calculated. 3~,,,V ' - - - ~ - - Raise IIII .. - - ~ r 415 | ~___...J Ovedoad Lower LS1 Lower [~l Raise Raise ~--o'-'~ LS2 Raise I\"-] I _ _ - - oL-1o3w\"e-r o--tI pi Lower (a) Electriccircuit Electric LS1 motor ~~ Top limit switch LS2 o - ~ Bottom limit switch Screw jack (b) Physical layout Figure 1.1 Electrical solution, based on three phase motor

4 Hydraulics and Pneumatics A hydraulic system A solution along hydraulic lines is shown in Figure 1.2. A hydraulic linear actuator suitable for this application is the ram, shown schematically in Figure 1.2a. This consists of a movable piston con- nected directly to the output shaft. If fluid is pumped into pipe A the piston will move up and the shaft will extend; if fluid is pumped into pipe B, the shaft will retract. Obviously some method of retrieving fluid from the non-pressurised side of the piston must be incorporated. The maximum force available from the cylinder depends on fluid pressure and cross sectional area of the piston. This is discussed further in a later section but, as an example, a typical hydraulic pressure of 150 bar will lift 150 kg cm-2 of piston area. A load of 2000 kg could thus be lifted by a 4.2cm diameter piston. A suitable hydraulic system is shown in Figure 1.2b. The system requires a liquid fluid to operate; expensive and messy and, conse- quently, the piping must act as a closed loop, with fluid transferred from a storage tank to one side of the piston, and returned from the other side of the piston to the tank. Fluid is drawn from the tank by a pump which produces fluid flow at the required 150 bar. Such high pressure pumps, however, cannot operate into a dead-end load as they deliver constant volumes of fluid from input to output ports for each revolution of the pump shaft. With a dead-end load, fluid pressure rises indefinitely, until a pipe or the pump itself fails. Some form of pressure regulation, as shown, is therefore required to spill excess fluid back to the tank. Cylinder movement is controlled by a three position changeover valve. To extend the cylinder, port A is connected to the pressure line and port B to the tank. To reverse the motion, port B is con- nected to the pressure line and port A to the tank. In its centre posi- tion the valve locks the fluid into the cylinder (thereby holding it in position) and dead-ends the fluid lines (causing all the pump output fluid to return to the tank via the pressure regulator). There are a few auxiliary points worthy of comment. First, speed control is easily achieved by regulating the volume flow rate to the cylinder (discussed in a later section). Precise control at low speeds is one of the main advantages of hydraulic systems. Second, travel limits are determined by the cylinder stroke and cylinders, generally, can be allowed to stall at the ends of travel so no overtravel protection is required.

Fundamental principles 5 A i ; ,, w B Raise (a) Hydraulic cylinder / /- Electric \\\\ // \\\\ /_ motor \\ // ('M) \"', Off \\\\ Raise q 9 9 Lower f ~ t/ H // H Pressure \"\\, ~ /w\\ ,'t Filter ~] regulation \"'. _g_ = I1 , I t=%2,, ~r ,......?;;J. ~ NEd I ,~ Pump ! I' - =xoe I fC, I I~ va've ~ ' I II II~- Components common L_. . . . . . . . . . . . . . . . . . . . J to many motions (b) Physical components Figure 1.2 Hydraulic solution Third, the pump needs to be turned by an external power source; almost certainly an AC induction motor which, in turn, requires a motor starter and overload protection. Fourth, hydraulic fluid needs to be very clean, hence a filter is needed (shown in Figure 1.2b) to remove dirt particles before the fluid passes from the tank to the pump.

6 Hydraulics and Pneumatics One final point worth mentioning is that leaks of fluid from the system are unsightly, slippery (hence hazardous) and environmen- tally very undesirable A major failure can be catastrophic. At first sight Figure 1.2b appears inordinately complicated com- pared with the electrical system of Figure 1.1, but it should be remembered all parts enclosed in the broken-lined box in Figure 1.2 are common to an area of plant and not usually devoted to just one motion as we have drawn. A pneumatic system Figure 1.3 shows the components of a pneumatic system. The basic actuator is again a cylinder, with maximum force on the shaft being determined by air pressure and piston cross sectional area. Operating pressures in pneumatic systems are generally much lower than those in a hydraulic systems; 10 bar being typical which will lift 10 kg cm-2 of piston area, so a 16 cm diameter piston is required to lift the 2000 kg load specified in the previous section. Pneumatic systems therefore require larger actuators than hydraulic systems for the same load. The valve delivering air to the cylinder operates in a similar way to its hydraulic equivalent. One notable difference arises out of the simple fact that air is free; return air is simply vented to atmosphere. l ]I Off I I I Raise Lower .. I -' Filter Air cooler Storage i (~ ? ? /~ I.~'r _i'k~ --,,, ~ and air reservoir I ~ ',I1' V~ ~-'l[t II ~ treatment / \\ I ~ B I] II ~ C o m p r e s s o r Pre.s..sure i [1c~1761U76~ ~ ...1. i~ sw,tcn I : PSI H PSI I I1 valve 1 3\"-'~~ ~ ~ Elettrr'c 1 II ~Exhaust I Opens when/ ...... J Components common [ pressure | to more than one motion II reached i L. . . . . . . . . . . . . . . . . . . . . . . . . . Figure 1.3 Pneumatic solution

Fundamental principles 7 Air is drawn from the atmosphere via an air filter and raised to required pressure by an air compressor (usually driven by an AC motor). The air temperature is raised considerably by this compres- sor. Air also contains a significant amount of water vapour. Before the air can be used it must be cooled, and this results in the forma- tion of condensation So, the air compressor must be followed by a cooler and air treatment unit. Compressibility of a gas makes it necessary to store a volume of pressurised gas in a reservoir, to be drawn on by the load. Without this reservoir, a slow exponential rise of pressure results in a similar slow cylinder movement when the valve is first opened. The air treatment unit is thus followed by an air reservoir. Hydraulic systems require a pressure regulator to spill excess fluid back to the tank, but pressure control in a hydraulic system is much simpler. A pressure switch, fitted to the air reservoir, starts the compressor motor when pressure falls and stops it again when pres- sure reaches the required level. The general impression is again one of complexity, but units in the broken-lined box are again common to one plant or even a whole site. Many factories produce compressed air at one central station and distribute an air ring main to all places on the site in a similar way to other services such as electricity, water or gas. A comparison Table 1.1 gives superficial comparisons of the various systems dis- cussed in the previous sections. Definition of terms There is an almost universal lack of standardisation of units used for measurement in industry, and every engineer will tell tales of gauges indicating, say, velocity in furlongs per fortnight. Hydraulics and pneumatic systems suffer particularly from this characteristic, and it is by no means unusual to find pressure indicated at different loca- tions in the same system in bar, kpascal and psi. There is, however, a welcome (and overdue) movement to stan- dardisation on the International System (SI) of units, but it will be some time before this is complete. The engineer will therefore encounter many odd-ball systems in the years to come.

8 Hydraulics and Pneumatics Table 1.1 Comparisons of electrical, hydraulic and pneumatic systems Electrical Hydraulic Pneumatic Energy source Usually from Electric motor or Electric motor or outside supplier diesel driven diesel driven Energy storage Limited (batteries) Limited Good (reservoir) (accumulator) Distribution Excellent, with Limited basically Good. can be system minimal loss a local facility treated as a plant wide service Energy cost Lowest Medium Highest Rotary actuators AC & DC motors. Low speed. Good Wide speed range. Good control on control. Can be Accurate speed DC motors. AC stalled control difficult motors cheap Linear actuator Short motion via Cylinders. Very Cylinders. solenoid. high force Medium force Otherwise via mechanical conversion Controllable force Possible with Controllable high Controllable solenoid & DC motors force medium force Complicated by need for cooling Points to note Danger from Leakage Noise electric shock dangerous and unsightly. Fire hazard Any measurement system requires definition of the six units used to measure: ~ length\" 9 mass; 9 time; 9 temperature; 9 electrical current; 9 light intensity. Of these, hydraulic/pneumatic engineers are primarily concerned with the first three. Other units (such as velocity, force, pressure)

Fundamental principles 9 can be defined in terms of these basic units. Velocity, for example, is defined in terms of length/time. The old British Imperial system used units of foot, pound and second (and was consequently known as the fps system). Early metric systems used centimetre, gramme and second (known as the cgs system), and metre, kilogramme and second (the mks system). The mks system evolved into the SI system which introduces a more logical method of defining force and pressure (discussed in later sections). Table 1.2 gives conversions between basic simple units. Table 1.2 Fundamental mechanical units Mass 1 kg = 2.2046 pound (lb) = 1000 gm 1 lb = 0.4536 kg 1 ton (imperial) = 2240 lb = 1016 kg = 1.12 ton (US) 1 tonne - 1000 kg = 2204.6 lb = 0.9842 ton (imperial) 1 ton (US) = 0.8929 ton (imperial) Length 1 metre - 3.281 foot (ft) - 1000 mm - 100 cm 1 inch- 25.4 mm- 2.54 cm 1 yard - 0.9144 m golum# 1 litre- 0.2200 gallon (imperial)- 0.2642 gallon (US) 1 gallon (imperial)- 4.546 litre- 1.2011 gallon (US) = 0.161 cubic ft 1 gallon (US)- 3.785 litre- 0.8326 gallon (imperial) 1 cubic meter- 220 gallon (imperial) = 35.315 cubic feet 1 cubic inch- 16.387 cubic centimetres Mass and force Pneumatic and hydraulic systems generally rely on pressure in a fluid. Before we can discuss definitions of pressure, though, we must first be clear what is meant by everyday terms such as weight, mass and force.

10 Hydraulics and Pneumatics We all are used to the idea of weight, which is a force arising from gravitational attraction between the mass of an object and the earth. The author weighs 75 kg on the bathroom scales; this is equivalent to saying there is 75 kg force between his feet and the ground. Weight therefore depends on the force of gravity. On the moon, where gravity is about one sixth that on earth, the author's weight would be about 12.5 kg; in free fall the weight would be zero. In all cases, though, the author's mass is constant. The British Imperial fps system and the early metric systems link mass and weight (force) by defining the unit of force to be the grav- itational attraction of unit mass at the surface of the earth. We thus have a mass defined in pounds and force defined in pounds force (lbs f) in the fps system, and mass in kilogrammes and force in kg f in the mks system. Strictly speaking, therefore, bathroom scales which read 75 kg are measuring 75 kg f, not the author's mass. On the moon they would read 12.5 kg f, and in free fall they would read zero. If a force is applied to a mass, acceleration (or deceleration) will result as given by the well known formula: F = ma. (1.1) Care must be taken with units when a force F is defined in lbs f or kg f and mass is defined in lbs or kg, because resulting accelerations are in units of g; acceleration due to gravity. A force of 25 kg f applied to the author's mass of 75 kg produces an accelera- tion of 0.333 g. The SI unit of force, the newton (N), is defined not from earth's gravity, but directly from expression 1.1. A newton is defined as the force which produces an acceleration of 1 m s-2 when applied to a mass of 1 kg. One kgf produces an acceleration of 1 g (9.81 ms -z) when applied to a mass of 1 kg. One newton produces an acceleration of 1 ms-2 when applied to mass of 1 kg. It therefore follows that: 1 kgf=9.81 N but as most instruments on industrial systems are at best 2% accu- rate it is reasonable (and much simpler) to use: lkgf=10N for practical applications. Table 1.3 gives conversions between various units of force.

Fundamental principles 11 Table 1.3 Units of force 1 newton (N) -0.2248 pound force (lb f) = 0.1019 kilogram force (kg f) 1 lb f - 4.448N - 0.4534 kg f 1 kg f - 9.81N - 2.205 lb Other units are dynes (cgs unit); 1 N - 105 dynes ponds (gram force); 1 N- 102 ponds SI unit is the newton\" N - kg ms-2 Pressure Pressure occurs in a fluid when it is subjected to a force. In Figure 1.4 a force F is applied to an enclosed fluid via a piston of area A. This results in a pressure P in the fluid. Obviously increasing the force increases the pressure in direct proportion. Less obviously, though, decreasing piston area also increases pressure. Pressure in the fluid can therefore be defined as the force acting per unit area, or: F (1.2) P = A\" Although expression 1.2 is very simple, there are many different units of pressure in common use. In the Imperial fps system, for example, F is given in lbs f and A is given in square inches to give pressure measured in pound force per square inch (psi). IF ~ P i s t o n areaA Fluid at pressure P = F/A Figure 1.4 Pressure in a fluid subjected to a force

12 Hydraulics and Pneumatics In metric systems, F is usually given in kgf and A in square centi- metres to give pressure in kilogram/force per square centimetre (kg f cm-2). The SI system defines pressure as the force in newtons per square metre (N m-Z). The SI unit of pressure is the pascal (with 1 Pa = 1 N m-Z). One pascal is a very low pressure for practical use, however, so the kilopascal (1 k P a - 1 0 3 p a ) or the megapascal (1 MPa = 10 6 Pa) are more commonly used. Pressure can also arise in a fluid from the weight of a fluid. This is usually known as the head pressure and depends on the height of fluid. In Figure 1.5 the pressure at the bottom of the fluid is direct- ly proportional to height h. i//////'/ h ~ Pressure in fluid at base: P = ph (psi or kg cm -2) P = pgh pascal Figure 1.5 Head pressure in a fluid In the Imperial and metric systems head pressure is given by: P - oh. (1.3) where p is the density and h the height (both in the correct units) to give P in psi or kg cm-2. In the SI system expression 1.3. is re-arranged as: P - pgh. (1.4) where g is the acceleration due to gravity (9.81 ms-2) to give the pressure in pascal. Pressure in a fluid can, however, be defined in terms of the equiv- alent head pressure. Common units are millimetres of mercury and centimetres, inches, feet or metres of water. The suffix wg (for water gauge) is often used when pressure is defined in terms of an equivalent head of water. We live at the bottom of an ocean of air, and are consequently subject to a substantial pressure head from the weight of air above

Fundamental principles 13 us. This pressure, some 15 psi, 1.05 kg f c m -2, or 101 kPa, is called an atmosphere, and is sometimes used as a unit of pressure. It will be noted that 100 kPa is, for practical purposes, one atmos- phere As this is a convenient unit for many applications 100 kPa (105 Pa or 0.1 MPa) has been given the name bar. Within the accuracy of instrumentation generally found in industry 1 bar - 1 atmosphere. There are three distinct ways in which pressure is measured, shown in Figure 1.6. Almost all pressure transducers or transmitters measure the pressure difference between two input ports. This is known as differential pressure, and the pressure transmitter in Figure 1.6a indicates a pressure of P]-P2. In Figure 1.6b the low pressure input port is open to atmosphere, so the pressure transmitter indicates pressure above atmospheric pressure. This is known as gauge pressure, and is usually denoted by a g suffix (e.g. psig). Gauge pressure measurement is almost uni- versally used in hydraulic and pneumatic systems (and has been implicitly assumed in all previous discussions in this chapter). Pressure ~P1 ~ Pressu re transmitter transmitter el P2 Hi LO Lo\"--'-- Opento Indication (P1 - P2) (a) Differential pressure atmosphere Indication (P1 - atmosphere) (b) Gauge pressure P, .... Pressure Vacuum transmitter n -i_ i, 1/~ Hi Lo \"--\"-- ii Indication P1 (c) Absolute pressure Figure 1.6 Different forms of pressure measurement

14 Hydraulics and Pneumatics Gauge Pressure being measured Absolute Atmospheric 0 . . . . . . . . . . . . . . . . Vacuum Figure 1.7 Relationship between absolute and gauge pressures Figure 1.6c shows the pressure transmitter measuring pressure with respect to a vacuum. This is known as absolute pressure and is of importance when the compression of gases is considered. The relationship between absolute and gauge pressure is illustrated in Figure 1.7. Pressure measurement and gas compression are dis- cussed in later sections. Table 1.4 compares units of pressure. A typical hydraulic system operates at 150 bar, while typical pneu- matic systems operate at 10 bar. Work, energy and power Work is done (or energy is transferred) when an object is moved against a force, and is defined as: work = force x distance moved. (1.5) In the Imperial fps system expression 1.5 gives a unit of ft lb f. For metric systems the unit is cm kg f. The SI unit of work is the joule, where 1 J - 1 N m (= 1 m 2 kg s-Z). Table 1.5 compares these, and other, units of work. Power is the rate at which work is performed: work (1.6) power - time\" The SI unit of power is the watt, defined as 1 J s-1. This is by far the most common unit of power, as it is almost universally used for the measurement of electrical power. The Imperial system uses horse power (Hp) which was used his- torically to define motor powers. One horse power is defined as 550 ft lb f s-1. Table 1.6 compares units of power.

Fundamental principles 15 Table 1.4 Units of pressure 1 bar- 100 kPa = 14.5 psi = 750 mmHg = 401.8 inches W G = 1.0197 kgf cm -2 = 0.9872 atmosphere 1 kilopascal - 1000 Pa = 0.01 bar = 0.145 psi = 1.0197 x 10-3 kgf cm -2 = 4.018 inches W G = 9.872 x 10-3 atmosphere 1 pound per square inch (psi) - 6.895 kPa = 0.0703 kgf cm -2 = 27.7 inches W G 1 kilogram force per square cm (kgf cm-2) - 98.07 kPa = 14.223 psi 1 Atmosphere - 1.013 bar = 14.7 psi = 1.033 kgf cm -2 SI unit of pressure is the pascal (Pa) 1 P a - 1N m -2 Practical units are the bar and the psi. Table 1.5 Units of work (energy) 1 joule (J) - 2.788 x 104 Wh (2.788 x 10 .7 kWh) = 0.7376 ft lbf = 0.2388 calories = 9.487 x 104 British thermal units (BTu) = 0.102 kgf m = 10 7 ergs (cgs unit) SI unit of work is the joule (J) 1J-1Nm = 1 m 2 kg s-2

16 Hydraulicsand Pneumatics Table 1.6 Units of power 1 kwatt ( k w ) - 1.34 Hp = 1.36 metric Hp = 102 kgf m s-1 = 1000 W 1 horse power (Hp) - 0.7457 kw = 550 Ft lb s-1 = 2545 BTU h-1 SI unit of power (and the practical unit) is the watt (W) Work can be considered as the time integral of power (often described loosely as total power used). As electrical power is mea- sured in watts or kilowatts (1 kW= 103W), the kilowatt hour (kW h) is another representation of work or energy. Torque The term torque is used to define a rotary force, and is simply the product of the force and the effective radius as shown in Figure 1.8. We thus have: T - F x d. (1.7) In the Imperial system the unit is lbf ft, in metric systems the unit is kgf m or kgf cm, and in SI the unit is N m. I | ~.=__ I Figure 1.8 Definition of torque

Fundamental principles 17 Pascal's law Pressure in an enclosed fluid can be considered uniform throughout a practical system. There may be small differences arising from head pressures at different heights, but these will generally be neg- ligible compared with the system operating pressure. This equality of pressure is known as Pascal's law, and is illustrated in Figure 1.9 where a force of 5 kgf is applied to a piston of area 2 cm 2. This pro- duces a pressure of 2.5 kgf cm-2 at every point within the fluid, which acts with equal force per unit area on the walls of the system. F=5kg Applied to area II A = 2 cm 2 Tank area = 1.5 m2 I I XProduces pressure ,Force = 37500 kgf ~_ P = 2 \" 5 kgfcm-2 , l LL, 9 ............ Base area 100 cm2 Force = 250 kgf (a) Forces and pressure in closed tanks Cork area a t Base area A (b) Pressure in a bottle Figure 1.9 Pressure in an enclosed fluid

18 Hydraulics and Pneumatics Suppose the base of the left hand tank is 0.1 x 0.1 m to give a total area of 100cm2. The total force acting on the base will be 250 kgf. If the top of the fight hand tank is 1 m x 1.5 m, a surprisingly large upwards force of 37,500 kgf is developed. Note, the size of the con- necting pipe has no effect. This principle explains why it is possi- ble to shear the bottom off a bottle by applying a small force to the cork, as illustrated in Figure 1.9b. The applied force develops a pressure, given by the expression: f P= . (1.8) a The force on the base is\" F - P x A. (1.9) from which can be derived: F-fx~. A (1.10) a Expression 1.10 shows an enclosed fluid may be used to magnify a force. In Figure 1.10 a load of 2000 kg is sitting on a piston of area 500 cm2 (about 12 cm radius). The smaller piston has an area of 2 cm 2. An applied force f given by\" 2 (1.11) f - 2000 • 5--0-0- 8 kgf. will cause the 2000 kg load to rise. There is said to be a mechani- cal advantage of 250. Energy must, however, be conserved. To illustrate this, suppose the left hand piston moves down by 100 cm (one metre). Because f = 8 kgf 2000 kgf 9 Figure 1.10 Mechanical advantage

Fundamental principles 19 we have assumed the fluid is incompressible, a volume of liquid 200 cm2 is transferred from the left hand cylinder to the fight hand cylinder, causing the load to rise by just 0.4 cm. So, although we have a force magnification of 250, we have a movement reduction of the same factor. Because work is given by the product of force and the distance moved, the force is magnified and the distance moved reduced by the same factor, giving conservation of energy. The action of Figure 1.10 is thus similar to the mechanical systems of Figure 1.11 which also exhibit mechanical advantage. f ~/////-/~t //f///i//21:~//////n (a) Lever (b) Pulleys (c) Gears Figure 1.11 Examples of mechanical advantage where a small input force f produces a larger output force F The principle of Figure 1.10 is widely used where a large force is required with small movement. Typical examples are clamps, presses, hydraulic jacks and motor car brake and clutch operating mechanisms. It should be noted that pressure in, say, a cylinder is determined solely by load and piston area in the steady state, and is not depen- dent on velocity of the piston once a constant speed has been achieved. Relationships between force, pressure, flow and speed are illustrated in Figure 1.12. In Figure 1.12a, fluid is delivered to a cylinder at a rate of Q cm 3 s-1. When the inlet valve is first opened, a pressure spike is observed as the load accelerates, but the pressure then settles back

20 Hydraulicsand Pneumatics ~V ,v @Close r///J'//-,,,ci t'~,.,,,-, n Inlet /~ Outlet Inlet Outlet ~lli~ valve k,L,) valve valve valve \" ~' '~ (a) Raising the load (b) Lowering the load Open V (if e > R) vInale,vt ~-[ L______f--I_ t Outlet I I LJ ]_ / J ~ Open valvep...~I.l Q--~ 0 ~ ! ; !~, ......... ! Inlet (~ Outlet .//'l/V Ia ' - D j valve ~ valve /I 1\\ (d) Pressure readings (c) Both valves open Figure 1.12 The relationships between force, pressure, flow and speed to a steady value of P = F/A kgf cm -2 where A is the area of the piston in cm 2 and F is measured in kgf. The load rises with a veloc- ity V - Q/A cm s-1 and velocity can obviously be controlled by adjusting flow rate Q. In Figure 1.12b, the inlet valve has been closed, and the outlet valve opened allowing R cm -3 s-1 to flow out of the cylinder. There is again a pressure spike (negative this time) as the load accelerates downwards, but the pressure reverts to P- F/A once the steady speed V - R/A cm s-1 is achieved. Finally, in Figure 1.12c both valves are open. The net flow is (Q-R) giving a cylinder velocity (Q-R)/A which can be positive (rising) or negative (falling) dependent on which flow is the largest. The steady state pressure, however, is unchanged at P = F/A.

Fundamental principles 21 Pressure measurement Behaviour of a fluid can generally be deduced from measurements of flow or pressure. A flow transducer or transmitter has to be plumbed, in line, into a pipe, whereas pressure transmitters can be added non-intrusively as tappings to the side of a pipe. The basic fault-finding tool in both pneumatic or hydraulic systems is therefore a pressure gauge. Often this is a simple gauge which can be plugged into various parts of the system via a flexible con- nection. These test pressure gauges invariably measure gauge pressure with the simple Bourdon pressure gauge shown in Figure 1.13. This consists of a flattened C shaped tube which is fixed at one end, shown in Figure 1.13a. When pressure is applied to the tube it tends to straighten, with the free end moving up and to the right. For low pressure ranges a spiral tube is used to increase the sensi- tivity. This movement is converted to a circular pointer movement by a mechanical quadrant and pinion. If an electrical output signal is required for remote indication, the pointer can be replaced by a potentiometer, as shown in Figure 1.13b. Hydraulic and pneumatic systems tend to exhibit large pressure spikes as loads accelerate or decelerate (a typical example being shown on Figure 1.12c.) These spikes can be irritating to the observer, can mislead, and in extreme cases could damage a pressure indicator. The response of a pressure sensor can be dampened by inclusion of a snubber restriction, as shown in Figure 1.13c. Bourdon gauge-based transducers are generally robust but are low accuracy (typically + 2%) devices. As the limit of visual reso- lution of a pointer position is no better than + 2% anyway, rugged- ness of these transducers makes them ideal for plant mounted monitoring. Where more accurate pressure measurement is required, transducers based on the force balance principle of Figure 1.14 are generally used. This is essentially a differential pressure transducer, in which the low pressure inlet (LP) is left open to atmosphere and the high pressure (HP) inlet connects to the system. The signal given (HP-LP) is thus gauge pressure. A pressure increase in the system deflects the pressure sensitive diaphragm to the left. This movement is detected by the displace-

22 Hydraulics and Pneumatics Cross section Toothed quadrant Pointer Pivot Increasing Linkage pressure Anchor block Pressure (a) Bourdontube gaugeconstruction Clockwise .~y DC+ Voltage reading o( pressure rotation for 0c- - increasing ~. ~ , pressure ? ' ~, DC- DC+ Slider (b) Electricalsignalfrom Bourdongauge ~ O rBgOauUgrdeon rifice Wire wool iction packing From t system From system (c) Snubberrestrictions Figure 1.13 The Bourdon pressure gauge

Fundamental principles 23 Pressure sensing diaphragm J , L HP Displacement Pivot transducer Diaphragm Balance ~ 9 ~ 9 o. -- Shunt Two-wire Required regulator 4-20 mA signal (mid) position amplifier o- Figure 1.14 Force balance pressure transducer ment transducer which, via a servo amplifier, leads to an increase in current in the balance coil. Because the force from the balance coil always exactly balances the force arising from the pressure difference between LP and HE current through the transducer is directly proportional to the differ- ential pressure. Remote indicating transducers are generally arranged with a remote power supply and the indicator and/or recorder connected into one line as Figure 1.15 to give a two-wire system. A signal range of 4 to 20 mA is commonly used, with the 4 mA zero level providing a current supply for the transducer's servo amplifier and also indicat- ing circuit continuity (0 mA indicating a open circuit fault condition). Fluid flow Hydraulic and pneumatic systems are both concerned with the flow of a fluid (liquid or gas) down a pipe. Flow is a loose term that gen- erally has three distinct meanings: volumetric flow is used to measure volume of fluid passing a point per unit of time. Where the fluid is a compressible gas, temperature and pressure must be specified or flow normalised to

24 Hydraulics and Pneumatics Chart Bargraph recorder + I= 4 mAto 20 mA I sp%upcwpleryI/ h. transducer Figure 1.15 Advantages of two-wire transducers some standard temperature and pressure (a topic discussed later). Volumetric flow is the most common measurement in process control mass flow measures the mass of fluid passing the point in unit time velocity of flow measures linear speed (in m s-1, say) past the point of measurement. Flow velocity is of prime importance in the design of hydraulic and pneumatic systems. Types of fluid flow are illustrated in Figure 1.16. At low flow veloc- ities, the flow pattern is smooth and linear with low velocities at the pipe walls and the highest flow at the centre of the pipe. This is known as laminar or streamline flow. As flow velocity increases, eddies start to form until at high flow velocities complete turbulence results as shown in Figure 1.16b. Flow velocity is now virtually uniform across the pipe. -v Velocitp~rofile _ v lhoiwghaat tw alls I Velocity'profile ,~ centre Turbulent uniform across pipe 9~ flow \\ (b) Turbulentflow fSlomwooth (a) Laminaror streamlineflow Figure 1.16 Typesof fluid flow

Fundamental principles 25 The nature of the flow is determined by the Reynoldsnumber, Rc, given by the expression: vdp (1.12) Rc = ~ r./ where v is flow velocity, d is pipe diameter, O the fluid density and r/the viscosity. The Reynolds number is a ratio and hence dimen- sionless. If Rc < 2000, flow is laminar. If Rc > 105, flow is turbulent. A turbulent flow is generally preferred for products in process control as it simplifies volumetric flow measurement (with differ- ential pressure flowmeters - see later). Turbulent flow, however, increases energy loss through friction and may lead to premature wear. Cavitation (formation and collapse of vapour bubbles) occurs with turbulent liquid flow and may result in pitting on valve sur- faces. Laminar flow is therefore specified for hydraulic and pneu- matic systems. This results in a desired flow velocity of about 5 m s -2. Energy in a unit mass of fluid has three components: 9 kinetic energy from its motion, given by ve/2 where v is flow velocity 9 potential energy from the height of the fluid 9 energy arising from the pressure of the fluid, given by P/O where P is the pressure and o the density. Fluid is passing along a pipe in Figure 1.17. Neglecting energy losses from friction, energies at points X, Y and Z will be equal. The flow velocity at point Y, however, is higher than at points X and Z ( ~ ~ (~'~ Pressure x , ,, , z Lowvelocity Low velocity high pressure high pressure Figure 1.17 Relationship between flow and pressure

26 Hydraulics and Pneumatics because of the smaller pipe diameter. Potential energy at each point is constant because the pipe is horizontal, so we can write: Vx2 +Px _ Vy_2_+ P_y _ V__z2+ _P_z (1 13) 2 /9 2 /9 2 /9 Energy Energy Energy at X at Y at Z We have implied an incompressible fluid by assuming the density, P, is constant throughout. Expression 1.13 becomes more compli- cated for a gas as different densities have to be used at each point. The net result of the expression is fluid pressure falls as flow velocity rises. Note, though, that the pressure recovers as flow velocity falls again at point Z. The simplest method of measuring flow (known as a variable area flowmeter) uses a float in a vertical tube arranged as Figure 1.18. The obstruction of the float causes a local increase in the fluid velocity which causes a differential pressure drop across the float, resulting in an upward force. The weight of the float obviously causes a downward force. The float therefore rises or falls depend- ing on which force is the largest. The area around the float, however, increases the higher the float rises because of the tube taper. This increase in area decreases the pressure drop across the float and the upwards force. The float therefore settles at a vertical Annulusarea ~~ ! pressure drop across float increases with height ~~~ Cross section ownwards force Figure 1.18 Variable area flowmeter

Fundamental principles 27 position where the weight of the float and the upwards force from the differential pressure exactly match. Flow rate can therefore be determined from the float position. A remote indicating flowmeter can be constructed from a pipe mounted turbine, as shown in Figure 1.19. Fluid flow causes the propeller to rotate, its rotational speed being proportional to flow rate. Blade rotation is counted electronically by an external induc- tive proximity detector to give an electrical signal for remote indi- cation of the flow rate. Pulserate AI.r'U'L Voltage frequency OCpulserate O(flow OCflow . ~ Electronic Proximity circuit detector ~J y Supports Turbine Figure 1.19 Turbinef/owmeter Finally, the classical method of measuring flow returns directly to expression 1.13 by locally increasing flow velocity with a delib- erately introduced restriction as shown in Figure 1.20. Typical obstructions are an orifice plate or a venturi. These increase flow velocity, causing a pressure drop which can be measured to give a differential pressure related to the flow. Unfortunately, the differen- tial pressure is proportional to the square of the flow rate, so a linear- ising square root extractor circuit is required to give a linear signal. Although differential pressure flow measurement is widely used to measure the flow rates of process material, the technique is not widely used in hydraulic and pneumatic systems. It will be apparent that all flow measurement systems are intru- sive to various degrees, and cannot be tapped in as easily as pres- sure measurement can. Fault finding in hydraulic and pneumatic systems is therefore generally based on pressure readings at strate- gic points.

28 Hydraulics and Pneumatics . . . . ~ Output signal --- (HP - LP) O( flow 2 I I I I Orifice II d/2 I I I I I I I ,,,,, Pressure Figure 1.20 Orifice plate flowmeter Temperature Fluid behaviour is determined to some extent by its temperature. A later section discusses the relationship between pressure and tem- perature in a gas. Temperature scales A temperature scale is established by choosing two observable physical effects which are dependent upon temperature and assign- ing numerical values to them. The Fahrenheit and Celsius (previ- ously known as Centigrade) scales use the freezing and boiling points of water as the two reference points\" Fahrenheit Celsius 0 Freezing point 32 100 Boiling point 212

Fundamental principles 29 From which: C (1.14) and: F - (9 x - i f ) + 32. (1.15) C - ( F - 32) x ~5. The SI unit of temperature is the Kelvin. This defines the lowest theoretical temperature (called absolute zero) as 0 K, and the triple point of water (0.01 ~ as 273.16 K. It should be noted that tem- peratures in Kelvin do not use the degree (~ symbol. These appar- ently odd numerical values make a temperature change of 1 K the same as 1~ and: K = ~ + 273.1. (1.16) The Celsius scale is most widely used in industry, but the Kelvin scale is important in determining the changes in gas pressure or volume with temperature. Temperature measurement There are four basic ways of measuring temperature based on tem- perature-dependent physical properties. Expansion of a substance with temperature can be used to produce a change in volume, length or pressure. This is probably the most common type of temperature measurement in the form of mercury or alcohol-in-glass thermometers. A variation is the bimetallic strip shown in Figure 1.21. where two dissimilar metals have different coefficients of expansion which cause the strip to Fixed Cold Hot, metal A expands more than metal B Figure 1.21 Bimetallic strip

30 Hydraulics and Pneumatics bend according to the temperature. This technique is the basis of most on/off thermostats used for temperature control or alarm annunciation. A bimetallic spiral can be used to construct an indi- cating thermometer. Electrical resistance changes with temperature. A platinum wire with resistance 100 ohms at 0~ will have a resistance of 138.5 ohms at 100~ Temperature sensors based on this principle are known as RTDs (for resistance temperature detector) or PT100 sensors (from PT, for platinum, and 100 for 100 ohms at 0~ Semiconductor devices called thermistors have more dramatic changes, the characteristics of a typical device being shown in Figure 1.22. The response, however, is non-linear which makes thermistors more suitable for alarm/control application than tem- perature indication. 5K \"E~\" 4K JE 9 3K U C \"~ 2K 1K 0 50 ~ 100 ~ Temperature (~ Figure 1.22 Typical resistance temperature curve for NTC thermistor Thermocouples, the principle of which is shown in Figure 1.23, use the small difference in contact potentials between different metals to give a voltage which depends on the temperature differ- ence between the measurement and reference points. Although widely used in process control, the technique is rarely encountered in pneumatic and hydraulic systems. The final method, called pyrometry, uses the change in radiated energy with temperature. As this has a minimum temperature mea- surement of about 400~ it is totally unsuitable for the systems we shall be discussing.

Welded Fundamental principles 31 junction V= f(T1,T 2) T1 ambient measured temperature temperature Figure 1.23 The thermocouple Gas laws For all practical purposes, liquids used in hydraulic systems can be considered incompressible and insensitive to changes in tempera- ture (provided the temperature remains within some quite broad limits). The gas in a pneumatic system is very sensitive to changes in pressure and temperature, and its behaviour is determined by the gas laws described below. In the following expressions it is important to note that pressures are given in absolute, not gauge, terms and temperatures are given in absolute degrees Kelvin, not in degrees Celsius. If we discuss, say, a litre of air at atmospheric pressure and 20~ being com- pressed to three atmospheres gauge pressure, its original pressure was one atmosphere, its original temperature was 293 K and its final pressure is four atmospheres absolute. Pressure and volume are related by Boyle's law. In Figure 1.24 we have a volume of gas V 1 at pressure P1 (in absolute units, PIV1 Figure 1.24 Boyle's law

32 Hydraulics and Pneumatics remember). This gas is compressed to volume V2, which will result in a rise of pressure to P2, where\" P1V1 - P2V2 9 (1.17) provided the temperature of the gas does not change during the compression. A reduction of pressure similarly leads to an increase in volume. In practice, compression of a gas is always accompanied by a rise in temperature (as is commonly noticed when pumping up a bicycle tyre) and a reduction in pressure produces a temperature fall (the principle of refrigeration). For expression 1.17 to apply, the gas must be allowed to return to its original temperature. Temperature Pressure indicator indicator Figure 1.25 Relationship between temperature and pressure In Figure 1.25, on the other hand, the temperature of a fixed volume of gas is controlled by a heater. A rise in temperature from T 1 to T2 results in an increase in pressure from P1 to P2, where: P~ _ P___2. (1.18) T1 T2 Again it should be remembered pressure and temperature are in absolute terms. Although expression 1.18 gives the change in pres- sure resulting from a change in temperature, it also applies to changes of temperature resulting from a change in pressure provid- ed no heat is lost from the system. In a pneumatic air compressor, the temperature of the outgoing compressed air is considerably ele- vated by the increase in pressure, resulting in the need for the com- pressor to be followed by an air cooler.

Fundamental principles 33 Expressions 1.17 and 1.18 are combined to give the general gas law\" P1V1 _ P2V2 (1.19) T 1 T2 where P1, V1, T1 are initial conditions and P2, V2, T2 are final con- ditions. As before, expression 1.19 assumes no heat is lost to, or gained from, the environment.

2 Hydraulic pumps and pressure regulation A hydraulic pump (Figure 2.1) takes oil from a tank and delivers it to the rest of the hydraulic circuit. In doing so it raises oil pressure to the required level. The operation of such a pump is illustrated in Figure 2.1a. On hydraulic circuit diagrams a pump is represented by the symbol of Figure 2.1b, with the arrowhead showing the direc- tion of flow. Hydraulic pumps are generally driven at constant speed by a three phase AC induction motor rotating at 1500 rpm in the UK (with a 50 Hz supply) and at 1200 or 1800 rpm in the USA (with a 60 Hz supply). Often pump and motor are supplied as one com- bined unit. As an AC motor requires some form of starter, the com- plete arrangement illustrated in Figure 2. l c is needed. There are two types of pump (for fluids) or compressor (for gases) illustrated in Figure 2.2. Typical of the first type is the cen- trifugal pump of Figure 2.2a. Fluid is drawn into the axis of the pump, and flung out to the periphery by centrifugal force. Flow of fluid into the load maintains pressure at the pump exit. Should the pump stop, however, there is a direct route from outlet back to inlet and the pressure rapidly decays away. Fluid leakage will also occur past the vanes, so pump delivery will vary according to outlet pres- sure. Devices such as that shown in Figure 2.2a are known as hydro- dynamic pumps, and are primarily used to shift fluid from one location to another at relatively low pressures. Water pumps are a typical application.

Hydrauficpumpsand pressureregulation 35 Fluid at -- or.ssor.I atmospheric Fluid pressure at high Pump (b) Pump symbol, arrow (a) Operation of a pump shows direction of flow rI Three phase II|I Motor LI .Motor control centre (MCC) I supply prote%ction II ~L ~ Starter 11---1:1\"--Start tl Electric I Stop Motor i motor eI ~ cu rrent II .-,(~-. running __J From tank Pump system Figure 2.1 (c) Pump associated components The hydraulic pump Inlet Outlet valve [_valve ~ Side view ' I1. / S ,, , , . _ -_\"_ f _ __V_ Top view illlllllJ (a) Hydrodynamic pump (b) Positive displacement pump Figure 2.2 Typesof hydraulic pump

36 Hydraulics and Pneumatics Figure 2.2b shows a simple piston pump called a positive dis- placement or hydrostatic pump. As the piston is driven down, the inlet valve opens and a volume of fluid (determined by the cross section area of the piston and the length of stroke) is drawn into the cylinder. Next, the piston is driven up with the inlet valve closed and the outlet valve open, driving the same volume of fluid to the pump outlet. Should the pump stop, one of the two valves will always be closed, so there is no route for fluid to leak back. Exit pressure is therefore maintained (assuming there are no downstream return routes). More important, though, is the fact that the pump delivers a fixed volume of fluid from inlet to outlet each cycle regardless of pres- sure at the outlet port. Unlike the hydrodynamic pump described earlier, a piston pump has no inherent maximum pressure deter- mined by pump leakage: if it drives into a dead end load with no return route (as can easily occur in an inactive hydraulic system with all valves closed) the pressure rises continuously with each pump stroke until either piping or the pump itself fails. Hydraulic pumps are invariably hydrostatic and, consequently, require some method of controlling system pressure to avoid cata- strophic pipe or pump failure. This topic is discussed further in a later section. A hydraulic pump is specified by the flow rate it delivers (usually given in litres min-1 or gallons min-1) and the maximum pressure the pump can withstand. These are normally called the pump capac- ity (or delivery rate) and the pressure rating. Pump data sheets specify required drive speed (usually 1200, 1500 or 1800 rpm corresponding to the speed of a three phase induction motor). Pump capacity is directly related to drive speed; at a lower than specified speed, pump capacity is reduced and pump efficiency falls as fluid leakage (called slippage) increases. Pump capacity cannot, on the other hand, be expected to increase by increasing drive speed, as effects such as centrifugal forces, fric- tional forces and fluid cavitation will drastically reduce service life. Like any mechanical device, pumps are not 100% efficient. The efficiency of a pump may be specified in two ways. First, volu- metric efficiency relates actual volume delivered to the theoretical maximum volume. The simple piston pump of Figure 2.2b, for example, has a theoretical volume of A x s delivered per stroke, but in practice the small overlap when both inlet and outlet valves are closed will reduce the volume slightly. Second, efficiency may be specified in terms of output hydraulic

Hydraulic pumps and pressure regulation 37 power and input mechanical (at the drive shaft) or electrical (at the motor terminals) power. Typical efficiencies for pumps range from around 90% (for cheap gear pumps) to about 98% for high quality piston pumps. An allowance for pump efficiency needs to be made when specifying pump capacity or choosing a suitable drive motor. The motor power required to drive a pump is determined by the pump capacity and working pressure. From expression 1.6: Power - work time force x distance time \" In Figure 2.3, a pump forces fluid along a pipe of area A against a pressure P, moving fluid a distance d in time T. The force is PA, which, when substituted into expression 2.1, gives\" Power - PxAxd T but A x d/T is flow rate, hence: Power = pressure x flow rate. (2.2) Unfortunately, expression 2.2 is specified in impractical SI units (pressure in pascal, time in seconds, flow in cubic metres). We may adapt the expression to use more practical units (pressure in bar, flow rate in litres min-1) with the expression: P o w e r - pressure • flow rate Kw. (2.3) 600 Pipe area A .... vi (\\ ')~' -.~ Pump Fluid moved distance d in time T Figure 2.3 Derivation of pump power

38 Hydraulics and Pneumatics For Imperial systems (pressure in psig, flow rate in gallons min-1), the expression becomes: Power- pressure x flow rate (2.4) 1915 Kw. For fully Imperial systems, motor power in horsepower can be found from: Horsepower = 0.75 x power in Kw. (2.5) Hydraulic pumps such as that in Figure 2.1 do not require priming because fluid flows, by gravity, into the pump inlet port. Not sur- prisingly this is called a self-priming pump. Care must be taken with this arrangement to avoid sediment from the tank being drawn into the pump. The pump in Figure 2.4 is above the fluid in the tank. The pump creates a negative (less than atmospheric) pressure at its inlet port causing fluid to be pushed up the inlet pipe by atmospheric pres- sure. This action creates a fluid lift which is, generally, incorrectly described as arising from pump suction. In reality fluid is pushed into the pump. Atmospheric Pump lift pressure ---.-~ To system I t .... L_ 1 Figure 2.4 Pump lift Maximum pump lift is determined by atmospheric pressure and is given by expressions 1.3 and 1.4. In theory a lift of about 8 m is feasible but, in practice, would be accompanied by undesirable side effects such as cavitation (formation and destructive collapse of bubbles from partial vaporisation of fluid). The lift should be as small as possible and around 1 m is a normal practical limit. Fluid flow in the inlet line always takes place at negative pres- sure, and a relatively low flow velocity is needed to reduce these side effects. The design should aim for a flow velocity of around 1 m s-1. Examination of any hydraulic system will always reveal pump inlet pipes of much larger diameters than outlet pipes.

Hydraulic pumps and pressure regulation 39 Pressure regulation Figure 2.5a shows the by now familiar system where a load is raised or lowered by a hydraulic cylinder. With valve V] open, fluid flows from the pump to the cylinder, with both pressure gauges P1 and P2 indicating a pressure of F/A. With valves V 1 closed and V2 open, the load falls with fluid being returned to the tank. With the load falling, gauge P2 will still show a pressure of F/A, but at P] the pump is dead-ended leading to a continual increase in pressure as the pump delivers fluid into the pipe. Obviously some method is needed to keep P1 at a safe level. To achieve this, pressure regulating valve V3 has been included. This is normally closed (no connection between P and T) while the pres- sure is below some preset level (called the cracking pressure). Once the cracking pressure is reached valve V3 starts to open, bleeding fluid back to the tank. As the pressure increases, valve V3 opens more until, at a pressure called the full flow pressure, the valve is Motor Raise (~ .Area A Pressure [~ Lower . Pressure regulating F/A valve F=mg (a) Circuitdiagram v, Ira,sol I I .... V2 (lower)- I I .... 7 1I I II I II I ,I 1 .,.J, I II i.... 1 I I I I I ,,IP1 V3setting ,,, (b) Pressurerecording Figure 2.5 Action of pressure regulation